Apparatus for multiphase vibration



June 11, 1940. R. w. BAM `2,204,007

PPARATUS FOR MULTIPHASEVIBRATION June 11, 1940. R. w. BAILY PPARATUS .FOR MULTIPHASE viRATIoN Filed Feb. 13, 1939 4 Sheets-Shet 5 Jazz June 1l, 1940.

R. w. BAILY APPARATUS FOR MULTIPHASE VIBATION Filed Feb. 13, 1939 4 Sheets-Sheet 4 t. WLWINHHHHMHHII. .tl I

Patented June l1, 1940 APPARATUS Foa MULTIPHASE vIBaATIoN anbei-:william Baiiy, Nal-berth, Pa.

Application February 13, 1939, serial No. s5052494 Claims. An object of my'inventon is to provide an apparatus for imparting to a material which b'e.

comes plastic, or increases in plasticity, when -vibrated, vibrations at higher frequencies than `heretofore available.

Thus one object of my inventionis to provide a simple apparatus for vibrating plastic materials, including a prime mover of comparatively lo low`speed, a vibrator and means for obtaining itself.

Another object of my invention is to provide an apparatus for imparting to a material which becomes plastic when vibrated, a plurality of frequencies, other, vibrations at higher frequencies, and if desired, still other vibrations at still higher frequencies, all from one apparatus. simultaneously.

`An object of my `invention is to provide a vibratory apparatus for utilizing a prime mover of comparatively low speed, and means for obtaining a high frequency of vibration in the vibratory member, and also a plurality of high. frequencies of vibration in the member simultaneously. My invention permits a new combi#- nation and utilization of some devices already obtainable on the open market, with other devices of my invention, to provide the step-up or increase of speed desired between v the prime mover and the out-of-balance weight or weights in the vibratory member, in order that the apparatus may be economical to manufacture and operate, and easy to repair.

A further object of my invention is to provide an internal vibrator more powerful in proportion to its weight and diameter than vibrators heretofore available, of` higher practicable frequency, y and to provide multiphase lvibrations which heretofore have not been available in one v apparatus.

Anotherobject of my invention is to provide an apparatus for expediting the chemical combination of various materialsby subjecting the molecules thereof to a` variety of high frequency Yvibrations simultaneously fromone mechanism, (obtaining a result similar to that obtained by the use of catalysts.

Portland cement concrete, for instance, contains four principal materials: Coarse aggregate, sand, Portland cement and water. materialsmay` be used in varying Drprtionaby 6- lection, the proportion of each 4which is intended best to accomplish the desired resulting concrete relatively high vibrating frequency in the vibrator phases of vibrations, some ofwhich are at highA taken into consideration the cost of the `ingredients, the ultimate crushing' and transverse l strength of the set concrete, the mpermeability and density of the mass, and so on.

At the time of combining these ingredients in amixture, and for a reasonable period thereafter, the mass becomes fluid and flowing when subjected to vibration. Obviously a certain proportion ofthe water is required for hydration of the cement. ,Additional water is usually placed inv the mixture to provide for lubrication of the mass to facilitate placing themixture in the forms or in its nal location. I have found that where vibration is applied to the mixture in the forms during the period o'f depositing the mixture, the proportionof water maybe greatly reduced, so that` with vibration a mixture `so stiff that it cannot otherwise be successfully placed by any ,other known method,fflows freely to position .while vibrated. Furthermore, entrapped air is liberated, .and even a large proportion of the re- `maining water is expelled from lthe mass.' The result is an extremely dense mass. I have also found that a considerable proportion of the cement can be omitted andthe resulting concrete will be stronger and denser than the riche'r mixes which are not vibrated.

I have also found that the larger particles in thezmixtureysuch as the coarse aggregate, are agitatedl best by comparatively low frequencies .of vibration that do not efficiently agitate the liner particles, such as the sand. I have also found that frequencies which best agitate the sand are too low toagitate efficiently the almost impalpable particles constituting thecement. I have found that by imparting to the mass a lvariety `of frequencies of vibrations simultanei ously, I am able to agitate all the particles of the mass in the most eiiicient manner. By the use of my method of imparting a pluralityrof phases of vibration at dierent frequencies to a given mass, I obtain a denser and stronger concrete, I am able' to reduce4 the proportion of the most expensive ingredient-cement-I am also able to place a given 4quantity of the material in a shorter time; I am able to accomplish this resuit-with less labor; and I am also able to remove the containing forms much earlier 4thereby reducing the'investment in form material since the forms'can be re-used sooner. Likewise I find size, certain frequencies of vibration cause f coarser and larger and heavier particles to coalesce, so that their combined mass causes these masses to beeiiiciently precipitated out of the liquid. I Ahave found that'smaller particles re-v main in suspension' andA that when I increase the frequency of vibration, these smaller particles,

in turn coalesce into larger` masses which are quickly precipitated out of the liquidi I have l0 found that when I impart to -the liquid two or more frequencies of vibration simultaneously, each frequency beingsuitable-for the suspended matterlit is desired to attack, thatthe different kinds of suspended particles are simultaneously caused to be precipitated from the liquid` Inv the manufacture of tinplate, for example, the oil used in the bath becomes heavily impregnated with impalpable particles of tin, iron vand other impurities of widely ranging sizes and specic gravities. I have found that I can cause the particles of iron to become precipitated by one frequency of vibration, and the tin particles by another frequency of vibration. By imparting both frequencies of vibration simultaneously, I am able to precipitate both metals during a single period of treatment.

I have also found that in the chemical industry there are manyprocesses in which it is desired to cause various chemical elements to combine rapidly. In many processes a catalyst is used to ments so closelyv together that the chemical action is expedited in the same manner as' if al catalyst were used without vibration. I have also found that Where catalysts are used, their action is expedited by the addition of Vibrations. 40 Also to be included among the objects of my invention is the provision of a flexible joint in the flexible shaft or cable which connects the vibrating housing to a motor in order that that shaft may -be made of any length and may beY hauled about a job without danger' of k'inking or otherwise damagingthe sli/aft` while in operation and contemplated with relation to this lb-fV ject is the provision of such a joint which can.'

by removing portions of the joint, be used to form` a flexible connection for thelvibratin'g housing itself. Theeiect in utilizing the devicein this way is that of .e flexible handle for the vibrating Lto engage corrugationsl! of the boss 9.' Extended through Sthezbore Il ofthe cap 1, I provide the g power shaft I4, whichinay` be rotated by the flexf ible shaft lconnected to any suitable source of j power.- A'jointlll incorporating a.k sliding drive 'spindle is shown connecting shafts :I I .and I5,- the element. A

With these and other objects in view, my inf' 55 vention consists in the construction, arrange- I -ment and'combinations of the various partsof.. my apparatus and in the practice of my methods,

' whereby the objectscontemplated are attained,

{onefo'rm of my apparatus. A

Figure 2 is a horizontal cross sectional view v65 of `my apparatus taken on line 2-2 o'f`Flgure; 1. 'Figure 3 is a vertical cross sectionalelevation *-fof'another form of myY apparatus;

-LpfFigureA is ahorizontal cross sectie-misill view s Figure is a'graph of the forces separately and'. combined Finnen .Y

` Figure ashow's a position of theweight 65 of .-15 i!il'lgur'eil.in the operation of thedevice.

Y,with Figure' 6.

generated in the 'apparatus of .Figure 5bvshows a later position of the weight of Figure 5a.

'Figure 5c shows a later position of the weight 65 of Figure 5b.

Figure 5d shows a. later position ofthe weightV 5 65 of Figure 5c.

Figure 5e shows a positionof the Weight 35a .of Figure A3 during the operation of the ap params.

Figure 5f shows a later position of that weight 4l0 during the operation.'

Figure 5g shows a still later position of the f weight 35a during such operation.

Figure 5h. shows a still later position ofthe weight 35a vduring such operation. 15

Figure 10 is a transverse crossvsection taken on line lll-III of Figure 8.

Figure 11 is an end elevational view of another form of my apparatus.

Figure 12 is an elevation of my apparatus, $0 equipped with a flexible handle.

Figure 13 is an elevation partly in section on the line l3-I3 of Figure 12, illustrating the attachment of the handle tothe vibrator casing. Figure V14 is a sectional view taken on the line I4-I4 of Figure 13, illustrating the manner in Vwhich two sections of the handle are connected to insurefree rotation of the encased shaft.

Figures 15 and 16 are a plan'view and sectional view, respectively, of the lockwasher used .40 in Figures 6 and 13. v. v v

Referring to Figure 1, I provide a housing l, which may be tubular in form, having the closed lower end 2. `Apin 3 is iixedwithln the end 2 and extends vertically from the inner, surface of the 45 .cap 2. The pin 3f terminates preferably in the,

frusta-conical end 5. 'I'he upper end ofthe housing AI is closed-by the end cap 'I engaging the.

housing I by threads 8 or by any other suitable means. Tothe upper boss 9 and cap 1 is secured 50 V`the sleeve Il held 'in .place' by the constricting means H, 'which causes-the materialv of sleeve 'II- details of which will lthe described in' connection 'The lower end IG shaft ll vterminates the fitting'll which arriestheinner race It of v -theballlbearingli whose Youter race' A2li is free;-

to' move butlnot rotativ'ely in the-.inner -I Vsurface-2 I" of the housing-fl. Abovegthe outer 65 race' 20"'and'bearingthereag'ain5t is vthe annular i i flange 2215i the nat pusherring 2 3.' -Above thefring I lI provide the pressure spring 24 which at its upper -vend presses v-against. :the lower facezfithe cap .1, and at itslower'end 7o -bears againstithe ring. The result is toc'ause the ring'lytofpressagainst the outer race 22.

and cause, it Atohave a 'tendencyv to Y move axially dewnwn'raigmeughrfthe 'beu bearing 'la this- Y,

vn iovenrenvt'istransmltted tothe fitting I1.'l 75 Y 4 vhousing I.

lExtending downwardly from the central part of fitting I1 are spaced ears 30 (one being omitted inthe dra'wing). The ears 30 carry the pin 3| which passes through the block 32, in a horizontal direction. The pin 3| passes through the body of apin 33 as well as through the block 32 and the ears 34 of the weight 35. The parts 3|),` 3|, 32, 33 and 34 forma universal coupling whose center of angularity 31 is at the intersection of the axis of the pin 3| with the long central vaxis in the 4 The weight 35 .is therefore free to oscillate inV any direction about such center, either laterally,` horizontally or with its axis 39 traveling a conical path about the axis 38 of the housing I. Likewise the weight 35 will revolve Aabout its own axis 39 at anlangular rateequal to the angular rate of rotation of the power shaft I4 about the axis 36.

At the lower endof the weight I provide i occurs at the point on the axis 39.

Within the weight' 35 I provide the bore 46 which receives the shank 41 of the crank 48, and the bore46 is concentric with axis 39. The cheek 49 of the crank 48 extends downwardly from its shank 41 and terminates'in the annular ring bearing 50 which receives the cylindrical portion of the pin 3. The axis of the bearing ring 5|! is the axis 38.

The shoulder 5| oi' the crank 48 does not engage the Weight 35. The crank 48 is provided with the boss 54 concentric with the axis 38 and engaging the end` of `the pin 3. Therefore the shank 41 of the crank 48 may move along the axis 39 within the bore 46 of the weight 35. It will beseen that tlfe face of the recess 4| makes the angle A with the axis 38 of the pin 3. It will also b'c seen that the crank 48 maintains the angle A, not permitting the angle to increase or decrease. Pressure'in the direction of the arrow 28A will therefore create a wedging action bringing` the face of the recess 4I into high pressure contact with the curved conical face of the pin 3. Pressure in the direction of the arrow 23A is provided by the pressure spring 24 of Figure 1 acting through the fitting I1, thence through the universal coupling to the weight 35. I make the spring 24 of such strength that it induces suficlent pressure at the point 43 to create rolling contact between the Weight 35 and the pin 3A and prevents sliding contact. Therefore as the weight 35 is rotated about its own axis 39, the face of the recess 4| must roll upon the tapered face of the pin 3. l

In Figure 1 I show the weight 35 having the recess 4| with its face making contact at the.

point 43 with the surface of the pin 3. I also show the cheek 49 which carries the annular bearing 50 engaging the pin 3.

In Figure 3 I show a modified form of my apparatus of Figure 1, the similar parts bearingthe same index numerals with the addition of a. In Figure 3 the power shaft |4a terminates at its lower end in the fitting ,I1a which carries the inner race |8a of the bearing |`9a whose outer race 20a-is freev to move axially but not rotatively in the inner surface of the. housing la. Extending below the fitting Ha is the eccentric weight l|5 which joins, with thefltting .|1a. The ring 69 l circle.

bears against the top of the outer race 20a. 'I'he upper portion 1| of the yring 69 has the Dockets 'l2 which contain the pressure springs 13. The springs 13 bear `against .the lower face of the cap 1a, and against the lower end of the pockets 12. causing the ring 69 to exert pressure against the outer race 26a. Through theballs and the inner race I8a this pressure is transmitted to the tting |1a, and thence through weight 65 to fitting `end of the weight is the fitting ring Hb (similar to |111) carrying an inner ball race lsb of a ball-bearing |9b having the outer race 20h movable axially but not rotatively in the housing la.

The center of gravity Y 66 (Figure 4) of the weight 65 travels in a circle 61 having its center in the long axis 38 of the housing la. The acceleration or centrifugal force of the weight 65 is in a direction radially from the center of that Operation Figure 5 is a graphor diagram showing the centrifugal forces Igenerated byn the weights 35a and 65 of Figure 3 as they revolve about the axis y 38, taking into account only those vectors of the forces perpendicular to one diametral plane on axis 36 of Figure 3, and showing the resultant vector sums at various vsequences of the revolutions of the weights 36a and 65.

It is obvious that the' radial distance of axis 39 from axis 39 remains constant, as shown in Figure 5e.` Therefore the axis 39 Willtravel in a circular path aboutthe axis 38. Based on the -relative dimensions chosen for this illustration, when the weight 35d is .revolved 120 degrees surface 4| of the Weight 35a will travel to location T2. Upon another degrees of revolution of weight 35a, point T1 will travel to location 'I'3 land so on.

It is later shown that with the relative dimensions chosen for this illustration, the axis 39 will travel around.' the axis 36 three times as fast.

as the rate of rotation of weight 65 about the axis 38. 7

Figure 5a shows the Weight 65 in a position generating force Fl of Figure 5.` As weight 65 revolves about axis 38 in Figures 5a., 5b, 5c and 5d,

it generates centrifugal forces of the magnitude i and directions shown/in Figure 5 at F1, F4, F1

Their vectors indirection of line RO generate the sine curve H of Figure 5. l

It will be noted that one position of the weight 65, as shown in Figure 5a is taken at the same instant as the position of the weight 35a of Fig-v ure 5e. y

When the weight 65 rotates from Vits position about its own axis 39, the point Tl on the inner shown in Figure 5a through ninety degrees to its -po'sition inFigure 5b, the weight 35a-'will rotate from its position inv Figure 5e, through 2'10 degrees to its position in Figure 5f. Likewise as the weight ss travels another ninety degrees to its position in Figurey c, the weight 35a will travel another 270 degrees t0 its position in Figure 5o.

The relative motions of the weights 65 and 35a continue in the same degree.

Thevector sum parallel to line RO of force generated by weight |5 shown as curve H of Fig- -ure 5 and force generated by weight 35d shown as curve F, produces the curve FH'. It will be seen that the housing la of Figure 3 will attain i a plurality ofphases of motion on one diametral Aplane passing through axis 38.l 'Similar phases l of motion at 90 degrees later time will be imparted to the housing la by the forces perpendic-L ular to a second diametral plane passing through axis 38 `vand located at ninety degrees angle from the first diametral plane. It will be seen that the housing la will vibrate in a plurality of phases or frequencies due to the difference between the,

120 degrees, theaxis 39 itself will have traveled in the same angular direction on the "circle I3 of the circumference of pin 3 through an arc of 360 degrees; in other words', the Yaxis 38 will revolve about the axis 38 three times as fast in angular measurement as theradius a revolves about its own axis 39.

If the `diameter of the pin 3 letter d, and the diameter ofthe wall or inner face of the yrecess 8| be denoted by the 'letter D, and if the revolutions per minute of the arrow 59 about the axis 39 be denotedrby `the letter P, and if the revolutions per minute of the 4axis 39 about the axis 38 be denoted by then i l O-PX D d Y In Figure 5', D was chosen as having a magnitude of 3 units, and d having a magnitude of 2 units, giving O=3P Obviously the center of gravity of the' weight lies at the point 45 of Figure v1 on the axis 39, and the acceleration or, centrifugal "force generated by the weight 35 is 4in theV direction .radlallyoutward from the axis of the housing as indicated by the arrow '6| ofV Figure Y1.

'Obviously any other` ratio Obviously the weight 65 revolves at' the samev angular rate as the shaftf I8, while, as shown in Figure 5, the axis 38 of theweight 35 will revolve three times, as VfastV in angular measurement aboutthe axis 38 under` the Vdimensions chosen for this description. Therefore the weight 35a will-make three' revolutions .about theaxls 38 for eachrevolution of the weight 55aboutfthe and d can beselectedto produce anyv desired rjeitive speedof the jweights :s and 6s, provided that D minus d is greater than unityfarid it will become apparent also'th'at the clrcumferensam'e litroportion as tial distances will have .the thediamete'r's.

The centrifugal force of the Aweigllt"35 ini the direction-of the arrow 8|, whichrrotates about the axis 38A in a' horizontal plane, imparts an oscillating motionto thehousing I, the, frequency vbe .denoted by lthe the letter` O,"

of the diametersD in the direction `of the arrow 6,8, which also revolves about the axis 38 in a horizontal plane, imparts an oscillating motion to the housing I,

the frequency of this x'notionl being theY same as thenumber of revolutions of the center of gravity 66 of the weight" 65 about the axis 38.

In Figure 5 at the right, I show diagrammatically the directions and magnitude of the centrifugal forces of the weights 35 and 65 of Figure 3, acting radially away from the axis 38 and revolving about the axisv 38. 'Ihe forces generated by the weight 35 are .vindicated by the arrows HI, H2, and so on up to IIIZ. Likewise l the forces generated bythe weight 65 are shown by the arrows F|,F2 and so on-up toVFIZ. These are taken. in sequence assuming rotation inthe directionofthe arrow 58. The vertical componentsfo'f'the forces are taken.inthe directions of the arrows 15 and 16.

In Figure 5 I have also shown diagrammatif cally the relation of the forceswith each other with respect t0 time. For instance, at the time 1 indicated'by RO the vertical component of Ithe force HI is zero and appears in Figure 5 'at HI on` the line RO. 'I'he vertical component ofthe vsaine forcelat H2 appears onv thev sine-curve at H2. and soon, generating the curve H which rises -to Hljthen passes downwardly through H1 tothe llow point Hill thence upwardly through HI on the line Rl, and continues in the s'ame manner. The distance aa to'bh represents the time involved in one revolution of the axis- 349.`

of the weight '35 about the axis 38 of theapparatuS. l Y

During thevsam'eperiod the vertical compo-f nents F of the force generated b y the weight 65 will form the sine-curve F of Figure 5. Since the weight 65 revolves, as assumedfor this illustration, at one--thirdv the speed of theweight 35,

the sine-curve'F will Ycommence'V with a valueof zero atthe line RO. will Vriseto Vthefpoint F4, thence go downwardly through'the pointjFI to the lowpint F|8 and rejoin the line Hat theV line R3. Y The,4 distance FRI indicates the time involved in one revolution Vof the weight 65, andV is equal in this illustration to the time required for three revolutions o the weightl 35.` L 1 The cumulative'eiect of the centrifugal forces generated by the weights 35 and 65are shown in the curveFH which isthe summation of fthe forces indicatedu bythe curvesF and The -l curve FH ,indicates the amplitude of movement,

imparted tothe housing I8 of Figure 1 by the revolvlnguweights 35 and 65;

-From this-'description it -wiuhe obvious 'that .that housing of Figure 3 will irnpartto any,y

material in which itis immersed, a variety Vof ,frequencieslof vibration and at various am- -plitudea' The relative rate -of rotation ,of the' weights 35- and 85 may be selected byvarying the diameters D and dof' Figurev 1,' so that any desired combination off frequencies and amplitude maybeobtained.- A, f

In Figure 6 is shown another form of my, apparatus.. The housing.. |88 =has-its lower end closed by Acap |82. and the upper end cap |83 4secu/red to the upper endofithe housing. Illll by the threadsill. Tothe upper bossl83a ofthe vcap |83 may besecureda sleevelike the Ysleeve |`8 abovel described. Infthe annular' bore |85 suitable source of power. 1

For the purpose or this description it may be I'.

considered that the power 'shaft |06 rotates clockwise when viewed from above.v Thelower part of the shaft |06 is somewhat enlargedas shown at |01 and theupper portion of such enlarged part is threaded.

The enlarged part |01 of the shaft '|05 is carried in anti-friction ball bearings |08 and has below them the annular shoulder |09 below which is the head ll0. The shouldered portion |09 carries the propelling ball carrier having the downwardly projecting circumferentially spaced lingers Illa.' A nut |I2 threaded on the upper part of the enlarged portion |01 of the shaft |06 clamps the inner race of theball bearing assembly |08 and the ball carrier ||l together to make them non-rotatable with respect to each other.

Within the housing and surrounding the iball bearing assembly and the upperpart of the ball carrier I|| is a sleeve II3. The sleeve |l3 is permitted limited movement lengthwise of the housing |00 but is held against rotary movement by means of a pin l|4 mounted in the wall of the housing |00 and projected into avertically elongated slot l l5 in the outer face of the sleeve l|3 at the upper end of the sleeve.

In the cap |02 is received a ball bearing assembly |l8 which is permitted certain movement axially of the housing |00. The bearing assembly I|8 receives the lower end of a shaft ||9. On the shaft ||9 below the bearing assembly IIB is a threaded nut |20. On the shaft ||9 above the bearings 8 is the out-of-balance weight I2| which has'fthe upwardly projecting spindle or `shaft |22 on which is a clamping nut |23 hereinafter again referred to.

The particular type of lock washer is designed for securing the inner rings of the bearing assembly |08 to the enlarged portion |01 of the` shaft |06. I'his construction takes'the form of la lock nut |l2 which is adapted to bethreaded upon the enlarged portion |01 in `order to press Y the inner rings of the bearing assembly against the upper surface of the ball carrier III. In order lto hold the lock nut in place there is provided a washer |60 which has a lug |6| in the' inner circumference thereof and a plurality of spaced lugs |62 at the outer circumference.

There is provided on the enlarged portion |01` a longitudinal slot |63 which extends beneath the inner ring of the bearing assembly and into this slot the lug I6| is projected to prevent rotation of the washer with respect to the enlargement.

The lock nut itself has provided therein a plurality of recesses |64 which are adapted to receive` the turned up ends of the outwardly projecting lugs |62 and thereby tightly lock the washer and nut in. place whenever the proper tenlll) . against movement downwardly. Above the inner race |25 is the separator ring |3| upon which sion has been placed upon the bearing assembly by screwing the nut downwardly upon the threadedsection of the enlarged portion |01. A

similar type of lock lower llock nut.

On the shaft |22 is the angular type ball bearwasheris used for the next ing indicated generally by the numeral |24. The f inner bearing |25 of the ball bearing |24 rests against the shoulder |26 of the weight I2I. The balls |21 with their carrier |28run in the outer race |29 which bears against a shoulder |30 in the housing |00, whereby theV bearing |24 is held rests the inner race |32 of a ball bearing indicated generally at |33 having the outer race |34 and the balls |35 engaged by the fingers Illa of the ball carrier ,l I I. Pins' |36 extend into the outer race |34 andinto the sleeve |33 and thus hold the outer race against rotation.

In Figure 7 is shown a section of the weight |2I. The center of gravity of the weight I2| is indicated by the point |31. The rotating axis of `the weightl2| is the same as the long axis 38' of the housing |00. Y

Before completing the description of the ball carrier III, I will refer to Figure 8 which shows a slightly modified form of device which may be used with the structure shown in Figure 6. In Figure 8 I have shown, instead of the power shaft |06, a power shaft |38 which is provided with the out-of-balance weight |39, the center of Where the shaft |38 and weight |39 are used and rotated, the' weight |39 will create a centrifugal force radially outwardly. The rate of angular rotation of the weight |39 about the axis 38' willbe the same as the rate of rotation of the shaft |06, Figure 6, under similar conditions. The rotation of the weight |39 will cause oscillation of the housing |00 at the frequency of rotation of the weight about the axis 38'.

Where the form of device shown in Figure 8 is used, aball bearing |4| shorter than the ball bearing shown above the ball carrier in Figure 6 is employed and below the weight |39 I provide a ball bearing |42 below which is a ball carrier |43 similar to the ballcarrier ciated with the balllbearing |32.

'Ihe sum of the affects ofthe two weights I2I and |39 upon the housing |00 corresponds exactly to the conditions and results described with the apparatus shown in'Figure 3. In otherl words, the arrangement of the device shown in Figure when equipped with the form of device shown in Figure 8 will produce multiphase vibrations and frequencies in the housing |00 which will in turn be transmitted to any surrounding material, such as concrete.

I will now refer to the operation and'construction of the ball carriers |Il'v and |43. Referring to Figure 6 it will be seen that the sleeve I|3 exerts a downward thrust against the outer ball race 34. The inner race may not move downwardly since it is supported by the separator |3| and the bearing |24. The balls |35 therefore' become wedged between the conical face |44.of'the outer race |34 and the conical face |45 ofJ-the inner race 32. The pres-` ||I and similarly asso- |32 of the same bearing 8 is the same as ball carrier of Figure 6. The I non-rotatable outer` race |34 engages and exerts pressure on the balls |35 at the points |41 and through the balls to the points I 48 on the inner ball race |32. As the shaft |06 rotates, the propeiling ball carrier |I I is rotated in the same angular direction. The Vfingers Illa of the ball carrier thus obviously rotate around the axis- 30" in the same angular' direction. The fingers Illa will exert pressure against the balls |35 andtend to move the balls in the direction indicated by the arrow |50. Since. the balls cannot slide in the races |34 and |32, they will rotate about their 75 ror placed on plastic material.

lrial whether in a form or container will be subcnters in the directionl indicated by the arrow Friction at the point |48 on the inner race |32 will cause the inner race to vrotate in the direction of the arrow |||v about the axis 38'.` 'I'he angular rate of rotation of the inner race |32 and the shaft- |22 which is fixed to the inner race will exceed the angular rate of rotation of the ball carrier 4and its shaftv|08.

'I'he amount by which the rate of rotation of the shaft |22 exceeds the rate of rotation of thc shaft |06 is'determined by the selection of the diameter of`the balls |35, the diameter of the inner face of the race |34 and the diameter of the face of therace |32 which engages the balls.

In the drawings I have selected dimensions in which the increase is in the ratio of 3 to 1 purposes .of my description.

Under the conditions` stated, the shaft |22! will rotate the weight |2| about the axis 38. three times'the angular rate of rotation of the power shaft |06. The direction of acceleration or centrifugal forceof the weight |42| is indicated by the arrow |49 in Figure '1 and the force will cause the housing |00 to oscillate at the frequency of rotation of the weight |2| about the axis 38?. The connection, therefore,4 between the vibrating portions of the shaft at this point is in the nature of a step-up or speed, change clutch adapted to drive the lower shaft at a greater `speed thanA the drive shaft. It can readily be housings I, la or |00 on a fom or container for plastic material o r' any member to be vibrated.

'I'he clamp has the members |5| and |52 adapted to be secured together by screw. bolts |53. The clamp member |52 has'a base |54 that may be bolted or otherwise secured to a form |55,

Thus the matejected to the single phase vibrations of the apparatus of Figures 1 and 6 or the multiphase" vibrations of the apparatus of Figures .3 and 8 when thev latter is used with the apparatus of Figure 6.

In vibrating apparatus of this sort which is operated by means of a flexible shaftor cable (Figure 12) it frequently becomes necessary ,to provide some means in thecable which will Y erally designated |12 comprising a part consisting of I.a mid section |12' and parts |19 and |14 connected to adjacent ends of theouter sleeve |`0' of the flexible shaft|18 as for example by use'of a' set screw |82.

'Ine-semble shaft usen is connues within the outer sleeve |0', one element of which is'indicated by the reference numeral |15 and* another -element of which is indicated by the reference character |15'. To provide the exible portion of the joint there is secured to the shaft element |15'for example a hollow sleeve |15 which is rotatably journalled within the casing |12 by means of ball bearing assemblies |11- and |18.

To the other shaft element |15 there is attached a projection |19 which extends in a somewhat telescopic like arrangement within the sleeve |15.

for the The sleeve is providedlwith a key extending inwards thereof and in the projection |19 there is provided an elongatedv longitudinal slot 8| adapted to receive'v the key |80 and permit it to move endwise'ther'eof while at the same time preventing relative rotation between parts. In an arrangement ofthis sort as the elements of the flexible shaft may be `shifted slightly in an endwise direction they are permitted freedom of movement while at the same time being se'- curednon-rotatably one withl the other.

A portion of the same connection can be utilized as a exible joint for the vibrating housing itself as shown in Figure 13. When the joint portionis to 4be used in this manner the part |18' A is retained while the remaining parts,

namely, the mid portion |12'A and |14 arel re-` |13' there is provided a .projection |19 to which f is attached an element of the exible shaft which leads from the motor.

When a vibrator housing such as 'the housingis attached in this manner it is provided with an end member |86 attached to the VhousingY at one end and attached threadably to the part |13' at the other. The vibrating., mechanism within the housing may Abe of the sort previously described-in this application, consisting primarily of ball bearing assemblies |91 operating about an enlarged partl |88 of a sleeve-like shaft element |89. Upon the shaft element there isattached the customary locking nut |90 together with the other portions of 4the device previously described, as shown lin Figure 13. The projection |19 `to which the flexible shaft element is attached is provided with an elongated longitudinal slot |9| similar to the slot |8| in Figure 14 and lthis slot is designed to receive a key extending zthereinto from the portion ofthe sleeve-like shaft element |89.

The operation of this flexible connection for the vibrator portion itself is similar to that described for the flexible joint shown in Figure- 14 in that the telescopic projection |19' and sleevelike shaft element |89 can move endwise with respect to each other but are fastened rnon-rotatably together so that there is a. positive drive from one to the other in a rotary direction.

In the operation of my method .Iinsert the apparatus either wholly or partially into thematerial to be vibrated, or I bring the apparatus into Y contact with a container containing the material, or I bring the aparatus into contact with the surface of the material to be vibrated, while the apparatus is vibrating. I may either allow the apparatus to remain suspended in, or in contact with the material, or in contact with the container, or I may move the apparatus about in orv on or against vthe material in a 'manner which I may deem will best accomplish the desired results.

In Figure 6 I show the lower end cap |02 carrying the pump screw |55 coincident with the axis 38'. In the shaft ||9, the weight |2| and the shaft |22 I provide thebore |51 slightlylarger in diameter than the screw |58. The screwA |56 lis provided with the threads whose pitch is in this case 4left hand." 'Ihe well |58 contains a lubricant, and as the weight |2| rotates, theA tween the weight |2| and the housing |00 through the bearings I I8.

Some changes may be made in the construction and arrangement of the parts of my device without departing from the real spirit and purpose' of my invention, and it is my intention to cover by my` claims any modified forms of structure, or use of mechanical equivalents, which may be ream `sonably included within their scope.

I claim as my invention: i

1. A vibrating device comprising a'v housing, a drive Vshaft journalled therein, a weight and a universal coupling for securing said weight nonrotatably to the shaft, a positioning pin for the weight secured within the housing, said weight being provided with a large tapered recess at the free end havinga surface therein of predetermined circumference and a complementarily tapered end on the pin'p'rovided `with a lateral surface having a circumference smaller than the circumference in the recess by a predetermined amount adapted to have one side held in rolling contact with one side of the surface in `said recess forming a crescent shaped space therebetween, a loose crank member positioned in said space having surfaces in sliding contact with the surfaces of said pin and said recess adapted to tilt the weight so that the center of gravity is displaced laterally'with respect to the axis of said shaft, and means for urging the surfaces into intimate Contact so thatas the shaft is rotated at a moderate speed the center of gravity of the i universally coupled shaft isrotated at a more rapid speed to produce high frequency vibrations in said "casing,

2. A vibrating device for producing vibrations at a plurality of frequencies comprising a housing, a drive shaft journalled in the housing, an off-center weight on said' shaft adapted to be rotated t'o produce vibrations of frequency cor- `responding to the rate of rotation of theshaft, `and asecond weight having the center ,of gravity positioned off-center with respect to the axis of the shaft loosely attached to the shaft and guided by a portion of said housing so that the center of gravity thereof is vibrated at a frequency different from that of the first weight'and producesl cumulative vibrations in the housing of a plurality of frequencies.

3. A vibrating `device comprising a housing, a" rotatable drive shaft journalled therein, a weight and a universal coupling for securing said weight non-rotatably to said` drive shaft,v a positioning pin in the housing adapted to hold the weight olf-centerV from the axis of the shaft, and coacting rolling contact surfaces on the weight and thepin adapted to cause rotation of the weight` and consequent vibration of the housing at a rate different from the rate of rotation of the shaft, and an off-center weight rotated synchronously with said shaft adapted jointly with said l rst weight to generatecompound vibrations of a plurality of frequencies in the housing. l

i fait vibrating device comprising a housing,v a rotatable drive shaft journalledv-therein, a weight and aiuniversal coupling for securing said weight non-,rotatably tothe shaft,`a positioning'pin for said weight secured within the housing adapted to tilt said weight so that the center of gravity thereof4 is off-center with respect .to the axis of' the `drive shaft, coacting tapered surfaces of different diameters on said weight and said pin adapted to form -a progressive rolling point of contact' therebetween and means for maintaining said contact sd that the axis'of the weight is to the axis of the drive shaft, saidweight being adapted -to be rolled about the positioning pin `at an angular rate different from the rate of rotation of saiddrive shaft to produce oscillating vibrations of adesiredfrequency in said housing and a second off-center Weight secured to the drive shaft adapted to be rotated at the same speedas the shaft and productive with vsaid first vweight ofv cumulative lcomposite vibrations `of a end on thepin providedwith a lateral surface having a circumference smaller than the circumferencein the recess by a predetermined amount adapted to have one side held in rolling contact with one side of thesurfacein said recessforming a crescent shaped space therebetween, a loose cranl-r,` member positioned in` saidspace having,`

surfaces in sliding contact with the surfaces. of said pin and said recess and having a surface in rolling contact with a surface on the pin, said crank member being adapted to tilt the Weight so that the center of gravity is displaced laterally with'respect to the axis of said shaft and means displaced at a predetermined angle with relation for urging the rolling surfaces into intimate contact so that as the shaft is rotated at a moderate speed the center Aof gravity of the universally coupled shaft is rotated at a more rapid speed to produce high frequency vibrations in said casing, and a second weight operatively secured to the vdrive shaft adapted to be driven at the same angular velocity as said shaft and adapted together with the first weight to set up a successive plurality of vibrations ofdifferent frequencies in said housing.

6. A vibrating device comprising a housing, a`

rotatable drive shaft connected thereto, an offcenter weight journalled in the housingadapted to be connected to the drive shaft to be rotated thereby in order to vibrate the housing, a connection between said shafts comprising a speed change member comprising bearing lrings and bearings mounted therein, one of said ringsrbeing connected tothe weight and another of said rings being mounted'non-rotatably with respect to the housing, means for shifting said rings longitudinaliy with respect to eachfother to wedge the bearings frictionally therebetween, and means for driving said bearings at an angular ra'te determined by the speed of the drive shaft, said bearings being adaptedto rotate and drive the inner of said rings and theV weight at an angular rate different from the driving means to set up a vibration of different frequency in the housing.

'7. A vibratingdevice comprising a housing, a rotatable drive shaft journalled therein, alweight V,shaft journalled in `the-housing adapted. to be connected to the drive shaft and an off-center weight adapted t`o be rotated thereby at an angular velocity differentA from said shaft Ain order to vibrate j the housing, a connection between said shafts comprising a speed changemember comprising a pair of bearing rings` and ,bearings mounted therein, one of said rings being connectedto the' -weight and another of said rings being mounted non-rotatably with respect to the housing and 'adapted to shift longitudinally with, respect to 75 8 v f v said first. ring to wedge the bearingszfrictionally therebetween, andme'ans on the drive shaft for driving said bearings thereabout atan angular rate of rotation determined by the speed of the drive shaft, said bearings being adapted to rotate in a lateral plane on theirrespective longitudinal axes and drive the inneriof said rings and the weight atan angular rate determined by the ratio vof the diameter of said bearings to the diameter of said inner ring to set up a vibration of diierent frequency by means of said weight.

8. A vibrating device comprising a housing, a rotatable drive shaft journalled therein, a weight shaft 'journalled in the 'housing adapted tobe t connected to the drive shaft and an off-center weight adapted to be rotated thereby at an angul lar velocity diiferent from said shaft in order to vibrate the housing, a connection betweensaid shafts comprising'a speed change member comprising aV 'pair of bearing rings and bearings'.

mounted therein, one of said rings being mounted on the weight shaft and another of said rings being mounted non-rotatably with respect to the housing and adapted to shift longitudinally with respect to said rst ring to wedge the bearings frictionally therebetween, means on the drive shaft for driving said bearings thereaboutat an angular rate of rotation determined by the speed of the drive shaft, said bearings being adapted to rotate in Aa. lateral plane on their respective longitudinal axes and drive the inner of said rings -andv the weight-at an angular rate determined Toy the ratio' of the diameter' of said bearings to the diameter of said inner ring to set upa vibration of different frequency by means of said weight, another oiI-center weight mounted on the drive shaft adapted to rotate simultaneously therewith and adapted further-to generate a set of vibrations at variance with said first weight and produce a compound vibration condition in the housing characterized by a succession of vibrations of varied frequencies.

9. In apparatus of the kind described, a housing having at one end a pin extending into the housing, a weight arranged for rotationl within the housing and having an interior track at one end concentric with the axis of rotation ofthe weight for rolling engagement with the pin, the

v diameter of the interior track exceeding the diameter of the pin, rotative means associated withy the Weightfor imparting rotation thereto, anti- .frlction means in the housingand engaging the weight and the pin for maintaining the axis of rotation of the weight in displacement with respectA to the axis of the pin, and, in addition to centrifugal force..pressure means causing rolling engagement oftheinterior track of the weight` with thepin at and immediately following commencement of rotation of the weight, the weight revolving onits axis of rotation at approximately the rate of rotation of the rotative means, the center of gravity and the axis of rotation of the weight revolving about the axis of the pin at an angular rate exceeding the rate'of rotation ofthe rotative means, causing impartationto the housing of vibrations at a frequency in excess of the rate of rotation of the rotative means.

10. In apparatus of the kind described, a member to be vibratedand having a pin disposed upon an axis of the .member, a weight -arranged for rotation about its own axis and valso -itbout the axis of the member, 'the weight havingan interior track at one end concentric with the weight axis `for rolling engagement with the pin, rotative means associated with the weight foiimparting rotation thereto; anti-friction means engaging the pin and the weight for maintaining the axis of the weight in displacement with respect to the axis of the member; and, in addition to Acentrifugal force, pressure means causing rolling engagement of the interior' track of the weight with the pin at and'immediately .following commencement of rotation of theweight, the weight revolving on its axis at approximately the rate'of rota- Q tion of the rotative means, the center -of gravity ofthe weight revolving about the axis of the member at an angular rate exceeding the rate of rotation of the rotative means, causing Aimpartation to the member-0f vibrations at a frequency in excess of the rate of rotation-of -the rotative means. ,l A

1l. In apparatus of the kind described, a housing having at one end a pin extending into the housing, a first weight arranged for rotation within thehousing and having an interior track at one end concentric with the axis of rotation of the first weight for rolling engagement withl at and immediately following commencement 0f rotation ofthe iirst Weight,\the first weight revolving on its axis of rotation at approximately the rate of rotation of the rotative means, the center ofl gravity and the axis of rotation of the first weight revolving about the axis of the pin at an angular rate of rotation of the rotative means, causing impartation. to the housing of vibrations at a frequency in excess of the rate of rotation of the rotative means, a second weight arranged for rotation within' and supported by the housing, the second weight having its center of gravity radially distant from its axis of rotation, said second weight axis of rotation being approximately coincident with the axis of the housing, the second weight being operatively associated with the rotative means to cause the second weight to revolve at approximately the 'speed of .rotation of the rotative means, the second weight.

imparting to the housing vibrations at a frequency approximately similar to the rate of rotation of the rotative means, whereby the housing is vibrated with a plurality of frequenciesof vibration. o

12. In an apparatus of the kind described, a

housing, a plurality of weights arranged forrol tation within the housing, a rotative means, each f weight arranged for coaction with the rotative means, each weight having its center of gravity radially distant from its axis of rotation, each weight so arranged that it imparts to the housing vibrations at a frequency similar to therate ofrotation of the center of gravity of the weight about an axis of the housing, means for causing the center of gravity of one or more of the weights to revolve about an axis of the housing at an angular rate' differing fromthe rate of jrotation of the center of gravity of'another 0f the weights about an axis of the housing, whereby the housing is vibrated with a plurality of frequencies of vibrations.

' 13. In an' apparatusfof the kind described, a

llneinber to be vibrated and a rotatableA l l driving shaft, a plurality of rotatable weights associated with the member, each weight arranged for rotation by the driving shaft, each weight having its center of gravity radially distant from the prolongation of the axis Vof the drive shaft, eaohweight so arranged that it imparts to the member vibrations at a` frequencyrsimilar to thel rate of rotation of the center of gravity of the, weight about the axis, means for causing the cening, a rst weight arranged for rotation within the housing and supported thereby, the first weight` having its center of gravity radially distant from its axis of rotation. a rotative means associated with the housing and-revolving the first Weight by means of an epicyclic train to. cause the first weight to revolve at an angular rate in excess ofthe rate of rotation of the rotative means, causing impartation tothe housing of vibrations at a. frequency' in excess of the rate of rotation of the rotative means, a second weight arranged for rotation within and supported by the housing, the second weight having its center of gravity radially distantfrom its axis of rotation, said second weight axis of rotation being approximately coincident with the axis of the housing, the second weight beingoperatively'- associated'with the rotative means in a manner to cause the-second weight to revolve at approximately the speed of rotation of the rotative means, the second weight imparting to the housing vibrationsv at a frequency approximately similar to the rate of rotation of the rotative means, whereby the housing is vibrated with a plurality of frequencies of vibration.

15. In an apparatus of the kind described, a

housing, a weight arranged for rotation within the housing and supported thereby, the weight having its center of gravity radially distant from its axis of rotation, a rotative means associated with the housing for revolving the weight and means for revolving the' weight from. the rotative vmeans comprising a speed-increasing epicyclic train having a fixed member, a `driving member ,i

associated with the rotative means and revolvin g at the angular speed of the rotative means, 20

a driven member associated with the weight and inducing rotation thereof, intermediate means making non-slidable engagement with the ilxed member and the driven member, said driving member propelling said intermediate means 25 causing the weight to revolve atan angular speed in excess of-the rate of rotation of the rotative means, thereby imparting to the housing vibrations at a frequency in excess of the rate of rotation of the rotative means.- i

Y ROBERT WILLIAM minar.` 

